Power transmission mechanism



Oct. 14, 1952 E. J. THURBER POWER TRANSMISSION MECHANISM '7 Sheets-Sheet 1 Filed April 50 1946 .mvziez' Oct. 14, 1952 E. J. THURBER POWER TRANSMISSION MECHANISM '7 Sheets-Sheet 2 Filed April 30 1946 3 rvu Win TM JZZzzrZe;

1952 E. J. THURBER 2,613,550

POWER TRANSMISSION MECHANISM Filed April 30, 1946 7 Sheets-Sheet 5 zi/ iii Zdzrardl'fzzrir) 3343 M AW Oct. 14, 1952 E. J. THURBER POWER TRANSMISSION MECHANISM Filed April 30, 1946 '7 Sheets-Sheet 4 JZZWZQ; L; (ram Oct. 14, 1952 E. J. THURBER POWER TRANSMISSION MECHANISM 7 Sheets-Sheet 5 Filed April 30, 1946 Oct. 14, 1952 E. J. THURBER 2,513,550

POWER TRANSMISSION MECHANISM Filed April so, 1946 7 Sheets-Sheet e 1952 E. J. THURBER 2,613,550

POWER TRANSMISSION MECHANISM Filed April 30, 1946 7 Sheets-Sheet '7 Q /45 If 2 1 1.25. 5 1 J6 J9 [Q Q Patented Oct. 14, 1952 POWER TRANSMISSION MECHANISM Edward Thurber, New Orleans,'La-., assignor to The Thurber Corporation, New Orleans, La., a corporation of Louisiana Application April. 30, 1946, Serial No. 666,064.,

59 Claims. 1,

The present invention relates to improvements in power transmissions adapted tobe employed for starting and controlling theoperation of machines and mechanisms generally, and isapplicable more especially to automobiles, motor boats and other. automotive vehicles for pro vidingvariable torque and speedjtransmission from an engine or driving means ,to the driven mechanism whichpropels the. vehicle.

The invention relates more particularly to power transmissions employing a rotor carrying hydraulic pumps interposed between the. driving and. driven elements of .the transmission and through. which torque. is transmitted between suchv elements by controlling the circulationof oil or other suitablefiuid through. the pumps.

One of the primary objects of thepresentinvention is to provide av novel. transmission of this type in which thehydraulio pumps perform the primary. function of building up the torque transmitted. from. the driving to the driven element, and thesecondary function. of developing pressure in the circulating. oil. or fluid to provide power for efiecting changes in speed ratios between the driving and-driven elements.

Another object is to. provide a. novel arrangement of governors controlled. automatically according to the speed of. the engine ordriving element and. the speed of the drivenelement ro spectively and which cooperates in. starting and gradually increasing the: speed of the. driven ele ment as the speed of the driving element isincreased, until the speed. of the driven. element has reached or nearly reached the speed of. the

driving element, whereupon the full torque of the driving element istransmitted. to the driven element.

Another object is to provide a'transmissionembodyingnovel: andimproved gearing for driving the driven -element atdifierent speed" ratios relatively to that of the driving element, and means for'chan'ging such gearing automatically, semi-automatically 'or manual-ly..

Another object is to provide a. transmission embodying gearing for changing the speed. ratio between the driving and driven elements,. and hydraulic means controllable at thewill. of the operator, for effecting changes through such gearing by power.

Another object is to provide novel and improved control means for a transmission of the type reierred. to for controlling the sequence of the gear changing operations.

Another'obje'ct is to provide a novel and im proved transmission embodying variable torque transmitting means, ,a. governor responsive to the speed of.:a' driven element of the transmission for controlling the torque transmitting means, and. gearing for providing different ratios of speed transmission from the torque transmitting means to the driven-element, andmeans -for set ting the gearing for' different, speed ratiosand coincidentally; setting the governor in acondition to lockthe torque transmitting mea'ns inra predetermined condition: when the gearing is set for one speed ratio and for setting the governor in an unlocked condition when the gearing is set for another speed ratio.

A further object is to provide .a noveland improved transmission embodying gearing including a member which is shiftableto. set the gearing for transmission of torqueat different speed ratios between the driving-and...driven elements. and a member shiftable in coordination with the shifting of said member of the gearing whenthe latter is .set for one speed ratio to condition the 7 transmission for. a change. to another speed ratio.

Aiurtherobject of the. invention is to provide a hydraulic power transmission mechanismv with circulating fluid to transmit. torque from the driving to the driven shaft at infinitely varying speed ratios. from zero to direct drive. the hydraulic transmission mechanism operating in conjunction with a. gearset having a plurality of forward gear rangesa reverse and a neutral conditionandlfijuid pressure or manually operable means to. select. or... effect. a gear range. change in thegear set, valvemeans. operable to control the fluid. pressure means, to effect a gear range change controlling. means for the. valve. means controlled conjointly by means responsive to the speed of the drivenshaftand modifiedby means responsive to. the throttlez controlling position of the. acceleratorpedal which operates the throttle of the engine; 7

Another ob-ject-of-the invention is to. provide a single planetary gear. set with. asingle -ring gear providing'a plurality of. forward gearran-ges, a reverseand a neutralwconditionz To; thesean'd: other ends; the invention consistsin certain improvements and combinations and arrangements of parts, allv as will be hereinafter more fully described, the features of novelty being pointed out: more particularly in the claims at the end of. thisspecification.

In the accompanying di'awings: I

Figure 1 is a side elevation, partly insection, of a power transmissiomembodflng the present invention; the? elements of the" transmissionbeing 3 shown in neutral position when the controls for the transmission are set for direct or overdrive.

Figure 2 is a longitudinal section through the transmission shown in Fig. 1, showing the elements in the relative positions they occupy while the transmission is in operation, and set in direct drive.

Figure 3 is a longitudinal section of the right hand end of the transmission shown in Figs. 1 and 2 on an enlarged scale, showing the transmission set in overdrive.

Figure 4 is a transverse section taken on the line 44 in Fig. 3.

Figure 5 is a detail cross section taken on the line 5-5 in Fig. 3.

Figure 6 is a transverse section taken on the line 6--8 in Fig. 2.

Figure 7 is a detail section taken on the line 1-1 in Fig. 2.

Figure 8 is a horizontal section taken on the line 8-8 in Fig. 2.

Figure 9 is a horizontal section taken on the line 9 9 in Fig. 1, showing the rails for setting the transmission.

Figure 10 is a view similar to Fig. 9, but showing the controlling rail shifted to set the transmission for direct and overdrive.

Figures 9a and 10a are diagrammatic views showing the positions of the setting member for the controlling rail when set in the positions shown in Fig. 9 and Fig. 10 respectively.

Figure 11 is a transverse section taken on the line ll-H in Fig. 9.

Figure 12 is a detail section taken on the line l2-l2 in Fig. 9.

Figure 13 is a transverse section taken on the line 13-43 in Fig. 9.

Figure 14 is a transverse section taken on the line M-M in Fig. 3, and showing the control means on the steering column.

Fi ure 15 is side elevation of a portion of the transmission, showing an interlock between the master edal and the rails which set the earing for different gear chan es.

Fi ure 16 is a detail transverse section taken on the line 16-46 in Fig. 2.

Figures 17 to 20 are detail longitudinal sections of the toroue pump controlling valves and adjacent structure, showing the valves in different ositions.

Sim lar arts are desi nated by the same referen e characters in the several vie s.

Al hou h the transmis ion mech n sm embnd n the resent in ent on is app icab e enera- 1y to th startin and o erat on of ma h nery of various kinds. it is sho n in the accom anyin drawin s and will be hereina ter described in detail as adapted for the control and operation of aut mobiles and other automotive vehicles. The preferred embodiment of the'invent on is sho n in the resent instance and will be hereinafter described, but it is to be understood that the in ention is not confined to the rec se construction sho n and described, as eq iva ent con truct ons are contem lated and such will be in luded within the scone of the claims.

As sho n in the present instance. the impro ed t ansm ssion com ri es a suitable casing for housin and sup orting the various ar s of the mechan sm, the casin pre erabl compris n an outer rotor casin sec on I. a control ca ng sec n an a tran m ssionear casin section 3. the e sect ons of th casin ein in ite or oth r ise secured. to' ether ri id v, he cas ng section l is con eniently formed to ho he usual'fiywheel 4 of an automobile engine which in the present instance is the driving element of the transmission, and the casing section 3 has the driven or propeller shaft or element 5 mounted therein through a suitable bearing 6. An intermediate shaft 1 extends between the flywheel or engine crank shaft 8 and the driven or propeller shaft 5, and. a main transmission shaft 9 is sleeved over the shaft 1' within the gear casing section 3 and is provided with a pilot l0 which is rotatably fitted in the adjacent end of the driven or propeller shaft 5, the other end of the shaft 9 being rotatably mounted in the casing section 3 by a suitable bearing ii, and this bearing supports the rear or adjacent end of the intermediate shaft 1 which is supported within the main transmission shaft 9 and is splined thereto by the splines 9a. The other or forward end of the intermediate shaft 1 is rotatably mounted in the rear or adjacent end of the flywheel or engine crank shaft 8 by a suitable bearing l2 which is preferably supported within a cylindrical extension [3 from the rear end of the shaft 8.

The intermediate shaft I carries a rotor 20 which houses a suitable number of hydraulic torque pumps, the rotor being conveniently housed within the flywheel 4 but is rotatable relatively thereto. Preferably, the flywheel is provided with an annular wall 2! which provides a chamber 22 for the rotor and also a reservoir for the oil or other fluid to be circulated by the pumps, removable plugs Zia being provided for the introduction of the oil or fluid therein. The rotor comprises a hub 23 which is fixed to the intermediate shaft 1 by bolting it to a flange E i which is formed integrally with said shaft, and a suitable number of circumferentially spaced arms or spokes 25 in which the torque pumps are housed, the outer ends of these arms being preferably connected by a circular ring 2E. The pumps are preferably of the gear type, each pump comprising a pair of pump gears 2'! and 23 which mesh and are fitted rotatably in a pump chamber 29 formed in the respective arm, each pump chamber having an inlet port 3% leading inwardly from the periphery of the rotor and a discharge or exhaust port 3| leading inwardly from the pump chamber to a valve chamber 32 formed in the hub of the rotor. One of the gears of each pump, such as the gear 27, has a shaft 33 fixed thereto and extending exteriorly of the pump chamber where it is provided with a driving gear 34, and these driving gears for the pumps mesh with a, gear 35 fixed to the driving shaft 8, as by forming this gear on the exterior of' the cylindrical extension [3 thereon. In order to prevent splashing or churning of oil or fluid in the rotor chamber 22 incident to relative rotation between the rotor and the flywheel and rotation of the gears 34, an annular splash shield 36 is fixed to the peri hery of the rotor and has a flan e which extends inwardly therefrom and partially houses these gears, the periphery of this shield having openings 31, however, to permit free communication between its interior and the rotor reservoir 22.

Each of the valve chambers 32 contains valves for controlling the circulation of oil or fluid through the respective pump. The valves in each of these chambers comprise an outer valve 40 preferably in the form of a sleeve which is fitted to reciprocate within the respective valve chamber, and an inner valve 4| which is reciprocable within the valve 40. Fach valve chamber 32 is open to the space in which the gears 34 operate,

5 anditheadjacentzend of the outer: sleeva valvojfl isiralsoropen thereto; The valve) is: provided wttlr. lateral ports 41 and 4:3 which: are movable, by reciprocation. of said valve; intmandi out of communication; wittranaxialcextension him of r the: discharge port; 31; and. with: a. port: Mi io'rmed radiallyjximthenrotorhabit-b and the-adjacent portion orf-thaintermediate shaft; 75,...frt a. purpose which. will;.hcreinaiter appear; The. inner: valve Mifits closely andzissrecipmcableinthe valmait andlcontrols thcport: 42;:in the: latter'vahzeg. and thsiinner valve, providsdwith a port. E: irrra side thereofrtcncontrol; communication between the port Manda. vent port. to in the valve. or.

Tl'lEiIOfiQI'? reservoir 22.? is. closed. atrits rear side by. a. casing: SBGUiDIlEZUi the: periphery of which is bolted or. otherwise secured to. the. annnlar wall 211?. and hasra. rearwardly. extending .hubxportion 531 1 WhiGhjiSz'llIiOE/idfidl.Wi'thifi; bearing'B-ZT in which aasleevez is: siigdablei axially. The. inner' of this sleeve; is .formcdr: with a. i'iairgo 54 through which: SiiBmsuFiS ,on'. the;- inner valves: 4t extend,

these. stemszatthe rear side or the flange 5 i havnuts: 58: or-other suitable adjustable abutments fiscdnthereom. these abutmentsbeing held yicldingiy' against therear side of. said flango "by springswcl'l'; onstencirclingveach: oi the inner valve stems; 55.; A second sleeve 60 extends. slida-bly through the sleeve 5*3fiai1diis :splined' onthe inter" mediate shafts]; thafor-ward end of this inner sleeve having a flangetsi thereon against which th flange 55 on: thezouter sleeve-isa-held yieidingl y by: the-springs 515,. and :therear ends of the outer valvesflit arehsl'ct againsttho -fla-nge t i for movement therewith bywthe springsrii 't. A spring 58 acting: on. the. sleeve 60 tends: to open the valves, a. i stop. springi is provided for limiting the extent, of opening thereof. Thecombined strengthi'ot. the springsfi'l is greater than the strength of". the. springv 64x, and the spring to is:stronger"-thanathe spring-5'8";

sleeve: 53 1 enteriorly of the rotor casing carriesa collar 351 with whichl ayoke 6G1 cooperates. for" shifting. thisvsieevo axially, said yoke bcingztormed preferably onthe inner'end of a levelr 6i which is. pivoted: within. the casing sect onxhfor rocking movement on a'p-i'v-o-t as; this lever extending: to: the outside of "this: casingsectiomwheresit is provided with a fork 6t for actuating itsin a.-.:mannerherci-naiter described. The siesta-tit alsol has" a coli'ar -or flange Tit fixed to the end; thereof exteriorly of thorotorcas-inga The; rotor casi rrg'section 56; which rotates-with and at. same speed as that of th engina or driving shaft 8, has a governor mounted therein. This-governorcomprises preferably a pai rof centrifugai governor members 'iS each of which is pivoted within the casing" section Silk at H and has azfinger iii which engages the; forward side of the flangetir on. the inner sleeve tit, and a weighted enclti which tendsto swing outwardly under-centrifiuga'la:force incident to rotation of the rotor, casing; As set screw or other suitable exteriorly adjustablev stop 80. is: provided in the rotor. casing; 01" limitin the. outward swing of each; fivernor: member, and'a spring 8& is provided for" each governor-member; this spring acting; to swing the; respective governor member outwardly against. its: stop; The power of each of these springs may be: adjusted by inserting an endthereoi; intoone-cr' another of aseries of holes 82: formediirrthe: weighted end. of the respective governor-member;

A secondto'r master governor cooperates the flange: it fixed to the inner sleeve 60-, this with 6 governor -comprisingc'prefrerablv a: suitable 51111111;- ber- 'oi centritugalzgovemor members" 8.5,; two -;of theseigovernoramembersibeingtshowrr intheipr'es cnt instance; These .governcrrmcmbers; are; no tat'ably mounted on pivots flfisupportsdby. forks 'I"f0rmed. ona. collar. 813: which is. fitted around the intermediate: shaft. 1 and; isflxcd; thereto-by screws 88 or other suitable means, spacers 8911 being interposed between saidi shaftandc opposite sides of the collarand through which the screws extend to provide spaces: 99; at. those: sides. ofrthe collar Whera theigovernor members: are mounted, and these sides orthe collar are-slotted; as. at 92! to permit thagovernor members to operate therein. Each: otthe. governor members-roomprises an arm flz adaptedf to cooperate. with the flange: it, and a weightedarm: .93. which ismovabl'ooutwardly under centrifugal force against theaction ofa spring 94, andthe strength of this spring may be adjusted by inserting: an end thereofinto onaor another of a-seriss or holes Sidin the weighted armt. Thescspringswill hold tho-governor members inthe retracted position shown in Fig. 1 while theintermediato-shait is not rotating, and centrifugal force will swing these governor members outwardly toward or to the position shown in Fig; 2 during-rotation of said shaft, causing the arms. 92 of the governor members to-actorr the fiahgaiii toshift the'va-lves til and 4i from the-position shown: in Fig 1 to- Wardonto the-positionshown' int-Fig. 2; according to thespeed of rotation of theintermediate shaft i Means isprovided; however, for-"overriding the master governor when desired; such means as shown in thepresent instance comprising a sleeve lilt which is slid'able axially on the shaft t and is splined to rotate there-with by tha -splines it i, this sleeve having-a pairof' segmental extensions on thereon which are movable in the spaces in the collar t8 and: engagea-blewith the heels of the governormembers 65-; movement ofthe sleeve lilo toward" the l'e'ft from the position s-hownin Fig; 2 causing theweighted endsof the governor members to swing inward-lyagainst theaction of centrifugal force and to cause the-arms 92' thereof to recede from tho flange 'i ii, thereby permitting the valves 35 and it to move'irom the position shown in Fig. Zto ortoward the-position shown in Fig; 1 under: theact-io-n of themain valve retracting spring 58; The sleeve [Hil is provided with a col-laror 15 3 which is fixed thereto and formed with a peripheral groove to receive the inner end of a shiftingarm iiii which is controlled andoperatod in amanner hereinafter described; In ordcr to stoprotation of the rotor or hold the rotorirom-rotaticn Whilethe main or master governor acts to hold thevalves 4i! and il in-retrac-ted position, the sleeve IEJQ' operates a brake which comprises in the present instance a friction brake ring m5 of suitable material which is fixed in a face thereof'and arranged to engage asim-i-lar brake ring iiitwhich is-fixed in an opposing face of a brake disk til-"i; the-latter being fixed non-rotatablyintl'i-e'casing-section 2, asby bolting-it to 'a-fiangeliit 'formed therein, the shaft i andsleeve H38- extending-"ireely through thisbrakedi'sk;

The transmission provided: b'ythe presentinvention combines therewith novel gearing containedin the casing section 3' which enables the ratio of" spced'transmissi'on between the rotor and-"thedriven orpropeller shaft 5. to bcchanged toprovidc'a; direct drive between these elements and to providean overdriveor'higher'ratio of speed of the driven or propeller shaft 5 relatively to that of the rotor, and to also provide a reverse drive between these elements. This gearing comprises in the present instance a sleeve I I which is mounted rotatably on the main transmission shaft 9. This sleeve is formed with a circular series of clutch teeth III with which a clutch ring II2 engages, and the main transmission shaft 9 is provided with a similar series of clutch teeth II3 with which the clutch ring H2 is engageable simultaneously with its engagement with the clutch teeth III when the clutch ring is shifted axially toward the left from the position shown in Figs. 1, 2 and 3, thus coupling the sleeve I I0 and main shaft 9 together. The sleeve IIO is also formed with a series of brake teeth II4 with which a complemental set of teeth II5 on a brake ring I I6 are engageable, as shown in Figs. 1 and 2. The brake ring IIG also has a second series of brake teeth I I1 thereon which i are engageable with a complemental series of brake teeth I I8 formed on a pinion carrier member H9 when the brake ring I I6 is shifted toward the left from the position shown in Figs. 1 and 2 to disengage the teeth H5 thereon from the brake teeth I I4. The brake ring I I6 is shiftable axially but is held from rotations in the casing section 3, as by splining it to an anchor I22 bolted or fixed in this casing section. The sleeve H0 is further provided with a sun gear I23 with which a suitable number of planetary pinions I2I mesh, these pinions being carried by the member H9 and a companion member lieu, these pinion carrier members being rigidly connected by the pinion shafts I23. The sleeve H0 is confined from axial displacement by abutting at one end against the flange on the shaft 9 on which the clutch teeth II3 are formed, and abutting at its opposite end against the pinion carrier member 3a which preferably is mounted rotatabiy en the main transmission shaft 9 and is retained from axial displacement thereon by a retaining ring I24 which may be inserted in a groove around the shaft 3. This pinion carrier member II3a is also provided on its rear face with a set of clutch teeth 25. The pinions I25 mesh with an internal gear I26 which is fixed to the driven shaft 5, preferably by forming it integrally therewith, and this gear is provided on the face thereof opposite to the clutch teeth I25 with a set of clutch teeth I21. A clutch member I28 is mounted between the pinion carrier member I I9a and the internal gear I20, this clutch member being slidable on the main transmission shaft 9 but connected to rotate therewith by splines I23, and this slidable clutch member is provided on its opposite sides with clutch teeth which are complemental to and engageable with the clutch teeth I25 on the pinion carrier member Il9a or with the clutch teeth I2? on the internal gear I26 when this clutch member is shifted axially in one or the other direction. The clutch member I28 is shown in its neutral position in Fig. 1, in its direct drive position in Fig. 2, and in its overdrive position in Fig. 3.

Means is provided for setting the clutch member I28 for operation by power and for operating it manually. As shown in the present instance, this clutch member, which is housed within the hub I26a of the internal gear I23, is provided with a peripherally grooved shifting collar I30 mounted on the gear hub I20a to shift axially thereon, and a shifting fork I3I which cooperates therewith, with screws I32 extending inwardly through the collar I30 and through slots I33 in place by a retainer band I54.

the internal gear and engaging in an annular groove I34 in the periphery of member I28, whereby movement of the collar I30 axially will shift the clutch member I28 correspondingly.

The power means for shifting the clutch member I28 derives its power from the torque pumps and associated spring means, and comprises in the present instance a shaft preferably composed of two sections I40 and MI which may be inserted into the respective ends of the hollow intermediate shaft I and connected at their inner ends by a pin I42 which is preferably located to aline with the screws 89, as shown in Fig. 5, so that these screws, while in place, will retain this pin in operative position, although when these screws are removed, the pin may be removed to disconnect the shaft sections I40 and MI and thereby enable the gear casing 3 and the gearing therein to be removed from the remainder of the transmission shaft I should such become necessary for any purpose. The end of the shaft section I4I adjacent to the clutch member I28 has a pin I43 extending diametrically therethrough, and this pin extends through diametrically disposed slots I44 in the adjacent portion of the main transmission shaft 9, and the ends of this pin extend into the holes I34 in the clutch member I28, thereby coupling the latter to the shaft section I4I for axial shifting movement thereby when said shaft section and the shaft section I40 connected thereto are shifted axially in the intermediate shaft I. This pin I43 is retained in position by the screws I 32 while they are in place, but may be removed, should such become necessary, by removing these screws.

The forward end of the inner shaft section I40 is preferably formed with an enlarged cylindrical collar I which is fitted to reciprocate in a cylindrical chamber I5I formed in the adjacent end of the intermediate shaft I, vent holes I52 being provided which extend from this chamber at one side of the collar to the exterior of the shaft 1, and a pair of packing rings I53 are provided at the other side of the collar and are retained in he Space between the packing rings provides a chamber which communicates with a port I55 which registers with the port 44 in the hub of the rotor, and with a port I55 in the shaft I which extends through the adjacent portion of the hub of the rotor and into the respective valve chamber 32, and continuations of these ports through the retainer band I54 communicate with an axial passage I5! formed centrally in the shaft section I40.

A sleeve I is fitted over the outer end of the shaft section I40 and is fixed thereto by a pair of pins IGI, and the outer end of the passage I5? is closed by a suitable plug I62. The sleeve I Gil carries a piston I 63 and a suitable packing I64 thereon which are reciprocable with a fluid tight fit in a cylinder I65 formed preferably in the adjacent end of the engine crank shaft 8. A relatively fixed cylinder head I86 having a suitable packing ring thereon is secured immovably in the cylinder I65, preferably by seating it agalnst an annular shoulder I6! formed in the cylinder and retaining it against said shoulder by the bearing I2 which is preferably an annular ball bearing and is pressed into the respective end of the cylinder. The shaft section I 40 and the sleeve I60 are provided with ports I68 which provide communication between the space within the cylinder I 65 between the piston I64 and cylinder head I63 and the axial passage I51 in said shaft section. 'Fluid pressure admitted to the axial passage 151 through the=port I55 or I56-will enter the space betweensaidpistonand cylinder head and ac-t to movethe piston and shaft sections I40 and MI toward .the Alert in Fig. Land tothereby shift theclutchmember I 2 B-into engagement with the clutch teeth 2 I25. on the pinion carrier member .I'Ida, as shown .in .3, any oil-or flni'clitrapped at the outeriside of the piston-being ventedtoitherotor chamber 22 through vent passages L69; and movementoi said .piston and shaft sections in the opposite direction, by =means1 to;be hereinafter described, will shift the .clutch .member (I28 to engage .it with the clutch :teeth vI21:ontthetinternalfgear I26, .as. shown in. Fig; 2, :anyroil DIAfiU-ICI trapp between the: collar I 510 and the adjacent end of the chamber .I5'I lacing ventedthroughithe ports I52 tothe exterior :of the shaft'1 where .it :may return to .the rotorcchamher. 22.

The-operations of the :clutch memberIIZBZar-e controlled .by.;a set .of rails I10, HI and I12, which are mounted to reciprocate in the -.upper portionzof .tire 'geaincasing -3. The shifting fork I3 I for this. clutch member; is; mounted loosely on the rail I between a collar I13 pinned .or-other- Wise .fixed to this; nail and. aspiring I14,which.;encircles this raihandabutsagainstwa-collar I which is pinned orotherwise fixed tosaid rail. Acsleeve l'ldhaving shifting .l-ugs I11 thereon-is loosely mounted on the rail Ito-between a cam I18 which is pinned or-otherwise-fixed tolthis rail and .a spring I19 which encircles this rail and abutseagainstthe collar.I13 fixed onsaid rail. Consequently, longitudinal movement. of the rail I10 in one direction .from :its normal ,neutral position shown in Fig. v1 will shift the clutch member I28 vinto driving-engagement.with the clutch .teeth 121 .on the internal gear I26 for direct drive between the rotor and theidriven shaft 2, andmovement ofthis rail intheopposite direction willshift said ,clutchmemher into driving engagement with the pinion carrier member I Ifiaiforoverdrive ,ordrive of .the driven or propeller shaft-.115 ata higher speedthanithat ofthe. rotor. The. rail; I12 .carriesajshifting. fork I86 which iszmountedi loosely thereon between'a collar l8! pinned on this rail. and a spring I 82, the latter abutting against a shifting jdcg I53 pinned .on the v rail 12, and havingoshifting lugs I84 thereon, an arm on the .shifting "fork I80 engaging 'in :a peripheral groove in the ,clutch ring-I I2. "While the transmission isset' in neutral position as shown in Fig. 1, oorfo'r'directcor overdrive'as in Elgar-2. 'or"3, respectively-the .clutc-h ring w'iilengageonlyrthe c'lutchiteeth I II on the main transmission shaft-Sand rotate id-1y" therewith, but-whenthe-rail I 12 is-shii ted to the left from theneutral position shown' in Fig- 9, the clutch ring I I I2 =will -brid ge or engage "both the clutch teeth I I land the clutch teeth I- IBM-hereby con-piing together the'main transmission shaft -d andit-hessleeve: I- to which carries themeverse gear I329 ,rthere-by cansinghthissgearktorrotate with .theirot-or. .PShif-t Of the railJI'1 #to the right or friomithei positions-shown in' Figii will shift-"the fork I80; through zthezspri-ngi m2; until the: clutch .7 I t2. has idisengagedgfrom :thezuteeth I I3= on shaft 9 "a to ;;'free :the; son igear from ithe ashaft whereupon a Llug 1:85 non :t-he 'fork'il iit -iabuts againstastop: pin I 86 fixed in the gear casing sectionan'd arrests further movement of fork I 80 toward the --right but further -'movement-'of the rail- I12 --wiil-be= permitted "by-compression of the-spring I82.

The-rail I1 I has "a shifting'dog I81 "pinned or otherwise fixed thereon, sthiS dog .carrying the brake ring .I I6,.and while the rail [II is in the position shown in Fig. 10, the clutch ring H6 will'be in the position shownin Figs. 1 and2 and will hold the-teeth I I5 on thebrake ring in engagement with the teeth ,IM on the sleeve III], thereby holding this sleeve from rotation since the brake ring is splined to the anchor member I22;fixed-in the gear casing :3, thereby holding the .sun .gear .120 .from rotation; and when the r-ailiii is shifted to the left from the positions-shown in'liig. 10 into theposition, shown infiige, the brake ring II-fi will be disengaged froin 'h'the braizeteeth I I I on thesleevel I0 and its brake vteeth H1 en ed with the brake .teetzh I518 on the pinion vcarrier member H9, thereby holding the pinion carrier from rotation and setting the gearing for direct and reverse drive; The dog I81 is controlledmanually by a hand lever :IIIII which is pivotedo-n anaxis ISI in any convenient .orremote position within;reach of theoperator, this leverbeing arr-angedto cooperate with either one of-a pair ofretainingnotches I9-2;an d I93 in a sector Ifii, thenotch I92'serving tohold this lever set'for reverse and-directdriving, and the notch I-93;for direct and'overdrive driving. This lever .is connected by suitable means to the dog lai as by a link Hi5 connecting itt-o one arm-ofa ,bell- -cranl lever [96 pivoted at I91 to a. suitable partofthe gearcasing 3, the other arm-of this bellzcr-ank lever :ex tending into the gear casing and-engaging a forlr I99 on -the dog I81. The doglm isalso provided with apairrof interlock lugs .2iiiland-2fil forra purposewhichwill hereinafter appear.

,The shiftingl-ugs I'84'on the fork-.I-83 -fixed to the shaft I12 are opposite to the shifting lugs I11 on the rail I10 while thelrails I11] and I12 are set for neutral as shownin Figs 9 .and;1f0. The rail I12 also carries .a transferm-ember 202 having a pair of longitudinally spaced lugs 203 and-2M thereomand the shiitingfork I3I on the rail I10 is provided with a lug 2B5 extending therefrom formovement between said-lugs. The lugs 203' and -2 I14 are so spaced,- apart and located relatively to the lug 265 that the rail I12 is free tOyShift to the left from the position-shoWn-in Fig. Q to engage theclutch member I I2 with the clutch teeth M3 on the main shaft .9 aswell as the teeth III on the sleeve III] which carries the I reverse driving sun gear .to set the gearing forreverse without contacting thelugZMwith the lug 20-5 projecting.from the fork I3I while the clutch member I28 is in neutral position, such shifting-movement of :therail I12 being limited by engagement of I the shifting dog I83 thereon against theadjaeent end wallpfthegear casing 3, but if the-clutch membenflflisengaged with the directdrive teeth I21, it will be disengaged therefrom and 7 set; in .neutral. The rail I12 also serves to -:manually ,set the clutch member 1min direct drive position by. movement of this rail toward the. right from its position asgshown in Fig. 9,, such movement, pf "t is rail bringing the lug 203 against the lug ,iiflion the shif in .iork I3I .end moving th .latter :fi direction to engage the; clutch member 7 I28 with theteeth IZT. on the gear I26 for .idiltect Qdrive. During such movement ofthe rail l12,1the,spring I82 willbe compressed,,duetoengagement ofthe stop pin I86 with the lug 1.85 on shifting fork I80, thereby permitting "the rail I1-2 to'shiftto a sufiicient extent'to place the gearing-in direct drive while the clutch ring I I-2 ispositioned over the clutch teeth II I.

Suitable interlocking means is preferably provided between the rails llD, HI and H2 to coordinate their operations. Such means comprises preferably a pair of plungers 2l5 and 2 which are freely movable endwise in an end wall of the gear casing 3 and notches or recesses formed in the sides of the rails to cooperate therewith. The rails Hi] and 172 each have a single notch 2l2 and 2H. respectively to cooperate with the outer ends of the respective plungers, and the central rail H! has a pair of notches 2&4 and H5 which are relatively offset longitudinally at the opposite sides of this rail. The notches 2l2, 2 i3 and 2M are so located along the respective rails as to receive the adjacent ends of the plungers while the rails are in neutral position but when the rails are set for a shift to reverse or direct drive, as shown in Fig. 9, the length of the plungers and the depth of the notches is such that the rail H0 is then locked against movement but the rail H2 is unlocked and free to be moved. When, however, the rail ill is shifted to the position shown in Fig. to set the rails for direct and overdrive, the plunger 210 is displaced from the notch 2l4 in the rail Hi and engaged in the notch 213 in the rail I12, thereby locking this rail from movement, and the plunger 2|! will be free to enter the notch 2l5 in the rail I'H, thereby unlocking the rail H0 for movement in either direction for a shift to direct or overdrive respectively.

The rails are shifted manually by a shift lever which is preferably mounted on the steering column of an automobile or other vehicle. As shown in the present instance, a shift lever 220 is provided having a pivotal connection by a pivot pin 22! with a shaft 222 which is mounted rotatably in bearing brackets 223 fixed to a side of a steering column 224, the lever having a casing 225 at its inner end which extends over the top of said shaft and beyond it and has a fulcrum portion 228 which bears on the top of the upper bracket. The shift lever is thus mounted for raising and lowering movement about the pivot pin 221 as an axis for swinging movement in an upper or lower are about the axis of the shaft 222 as a center, thus simulating the movements of the conventional gear shifting lever of an automobile, and the shaft 222 will be raised or lowered by such raising or lowering movement of the shift lever. A shifting shaft 221 is mounted rotatably in the upper part of the gear casing 3 above the rails, and an end of this shaft extends to the exterior of a side of said casing and has an actuating arm 228 pinned or otherwise fixed thereto. This arm is provided with a slot 229 in which an arm 238 fixed to the lower end of the shaft 222 engages, whereby swinging movement of the shift lever 220 in one or the other direction will swing the arm 228 and thereby rock the shaft 227 in one or the other direction. A shifting arm 23! is provided on the shaft 22'! and is engageable selectively with the shifting forks on the rails ll'il and I12 and is rotatable with said shaft to reciprocate the selected rail. As shown, this arm is formed with a sleeve-like hub 232 which is slidable longitudinally on the shaft 22'! but is splined to rotate therewith by a key 233 in the hub which engages in a keyway formed longitudinally in the shaft. Preferably, the shifting arm 23| is normally and yieldingly engaged with the rail ITO, it being held in such engagement by a spring 235 which is interposed between the hub of this arm and the adjacent side of the gear casing, this spring being yieldable under manual effort applied to the gear shift lever 220 to raise it to permit transfer of the arm 231 from the rail H0 to the rail H2, such transfer being accomplished by upward movement of the shaft 222 through a grooved collar 235 fixed on said shaft and engaged by one arm of a bell crank 23? mounted on a fixed pivot 238, the other arm of this bell crank being connected by a link 239 to an arm 245 fixed to the hub 32 of the shifting arm 23!. The spring 235 normally holds the shifting arm 23! in engagement with the fork ill on the rail Eli thus setting the transmission for manual shifting into direct or overdrive and from overdrive to direct drive by shifting this rail in one or the other direction.

Means is provided for effecting shifts from direct drive to overdrive and from overdrive to direct drive under control of the fuel control element of the engine in conjunction with the master governor 85, preferably the usual accelerator pedal of an automobile. For this purpose, the sleeve Hill is provided at its rear end with a tapered or cam portion 245 which is engageable with a radially arranged plunger 246 mounted slidably in the adjacent wall of the gear casing 3, this plunger being pressed by a spring 24'! into engagement with said cam portion at its inner end and acting at its outer end on a ball 248 and pressing the latter against the cam H8 which is pinned or fixed on the rail I'll] and has a rounded end 249 and a groove or recess 25B adjacent thereto with one or the other of which the ball 248 is engageable under the pressure of the spring 241. The power of this spring when compressed is suificient to move the cam H8 and rail llil to the right when the ball 248 engages the rounded end 249 of cam I78, or to cause a snap action of rail I10 to the left when the ball 248 approaches recess 255. While the transmission is set in neutral, the ball 248 is pressed against the side of the cam I18 between the groove 250 and the adjacent rounded end of the cam, as shown in Fig. l, and while the transmission is set in direct as shown in Fig. 2, this ball is pressed against the rounded end of the cam, and when the transmission is shifted to overdrive, this ball is engaged in the groove 250, as shown in Fig. 3, thereby locking the transmission in overdrive.

The shifting fork I54 for the collar I53 fixed to the sleeve I00 is mounted loosely on the rail Ill and held yieldingly against a stop collar 253, pinned or otherwise fixed to said rail, by a spring 254 which is interposed between this fork and a collar 25'! fixed to the forward end of the rail I'll. The rail H2 has an arm 255 pinned thereon, this arm extending beneath the rail Ill and spring 254, and an arm 258 extends loosely over the rail I15, and is in a position to be engaged by the arm 255, the arm 258 being fixed rigidly to a slide 259 guided to reciprocate longitudinally of the transmission by suitable guides 26!! which may be secured to the under side of the top or cover of the control casing section 2, springs 26| and 262 being interposed between the respective sides of this arm and collars 253 and 254 which are pinned or otherwise fixed to the rail I16. The slide 259 carries a plunger 265 which is normally held yieldingly in a raised position by a spring 266, this plunger being located below the forward or toe end of the fuel control element or accelerator pedal 261. The accelerator pedal corresponds to that commonly employed in automobiles for controlling the operation of the engine, it being pivoted at 268 on a suitable fixed bracket 269 to rock forwardly and rearwardly, it being 13 connected to la throttle operating arm 21!! which is-suitably connected, :as by .a .link 2H and a lever 212 pivotedat213 on the transmission casing, to a rod 214 which operates the throttle 215 of the carburetor 2l'6 which supplies fuel to the engine. Inapplying the present invention to an automobileequipped with such a throttle or accelerator pedal, the operating rod 214 is provided with springs 21? and 218 which areinterposed between the respective sides of the carburetor lever 219 and a pair of collars 28i) and-28l which are :fixed on the rod 214, thereby permitting this rod'and the accelerator pedal connected thereto to be operated beyond the fully open or fully closed throttle position, openingand closing movements of the throttle operating lever 2l9 being limited b'y-suitable stops 282 and 2821 respectively.

Below the plunger 265 are mounted a pair of bellcrank levers 285 and 2 86 which are pivoted t'o-rock on pivots 211i and 288 respectively, the arms 2'89 :and'ZGil of these bell crank levers extending toward one another, and-a separating or holding member 29! being fixedto a side of the casing and "extending between the adjacent. ends of the arms 2 8B and 29%. By this structure, while the plunger 2-55 occupies the position shown in Fig. l lnwhich the transmission is in neutral, the lower end of this plunger will be directly above the member 29! so thatdepression of the plunger willnot operate-either of-said bell cranks, but while the transmission is in direct drive, as shown in Fig. 2, the. plunger 265 will occupy a position above the arm 2% of the bell crank 28% and at one side-of the member29l, so thatdepres'sion of said plunger will rock this bell crank onits pivot, and while the transmission is in overdrive, as shown in Fig. 3, the plunger 255 will occupy a position-above the arm 289 of the bell crank 235 and at the otherside of the member 29l so that depression of said plunger will then rock the bell crank 285 on its pivot.

I hesetting of the. plunger 265 in these different positions is controlled by the setting of the rail I10. 1 For this purpose, the bell crank 285 has its otherarm pivotally connected to a rod 295 which extends loosely throughan opening 296 in the shifting fork Hi4 and has a head 291 fixed thereon to engage the rear side of said fork. This loose connection permits the sleeve Hill and its shifting collar I03 to-move forwardly independently of the bell crank 285 .and plunger 255 but connectsthe forlk I04 for movement forwardly when the lbellhcrank2il'5 is rocked by depression of the plunger 265. The bell crank 286 has its other arm pivotally connected to a rod298 which extends loosely throughan opening 259 in the lever 61 and has a head 300 fixed thereon to engage the forwardsside of saidlever. The throttle operating rod '2'II extends loosely through the fork 69 on the lever 67 and has a collar 3M adapted. to be'fixed thereon in a position to abut against the upper endof said :lever when the-accelerator-pedal -is rocked. rearwardly in a closed throttle direction to :or beyond. its. fully closed throttle, position,.and during such operation of theaccelerator -pedal, the lever B l- .is rockedab out its pivot: 68 ina direction to :retract theusle'eve 53, thereby retracting the inner. valves 4 I and also, through the springs 51, the outer valves 4E! against the action of the spring '64, thus shifting the valves 40 and 4| from their normal partially open position as shownin Fig. 1 to or toward their fully open positionas shown in Fig. 18. The leverfil also has-an-arm 3U5-fixed thereon and projecting rigidly therefrom in a position to be A master control member, operable at thewill of the operator, is provided for over-ridingthe master governor and all of'the other controls and for applying the brake to retard or look the driven or propeller shaft 5 from rotation, :this member preferably comprising a pedal =3!!! Which is mounted on a shaft 3| I rotatable in the lower portion of the casing section'2, this'sha'ft having a shifting dog 3 I 2 keyed orotherwise fixed thereon and arranged to engage andshift the collar iii-3 forwardly against the :action of the spring 25 thereby shifting the sleeve It!) forwardly to relieve the spring pressureon the ball 2 l8land thus release the cam Hi8, permitting the shaft lid to shift under the action of vthe springFt-"I-d from the overdrivesetting shown in Fig. 3420 direct drive as shown in Fig. 2, and :alsooausing the extensions I92 on the forvvard'end' of the sleeve We to over-ride the master governorland to push the members 93 thereof, againstcentrifugal force, toward their retracted position, thus permitting the spring 58 to retract the sleeve-8U and thereby pull the valves M3 and M 'into the open position shown in Fig. 1. In order, however, to permit shifting of-the sleeve I 00 by the-setting of the rail il independentlyof the master pedal, the latter is preferably mounted loosely onthe shaft til so that said'shait may be rotated in a direction to advance the sleeve Iiiil while the masterpedal remains in an inactive position, and a dog 3&5 is keyed or fixed to the shaft 34 I and provided With'an arm tit-arranged in the path of the pedal to be engaged and operated thereby When the master pedal is depressed.

An interlock is provided between the master pedal and the 'transmissionsetting or operating shaft 22? to prevent setting or operation'of the transmission unless the master pedal'is depressed. Such interlock comprises preferably :azplunger 320 mounted slidably in-a suitable bracket 32I fixed to the adjacent side of the transmission casing and loaded by a spring 322 which acts to press this plunger into one or another of a set of notches 323, 32 i and 325 formedin asegment-like portion 326 formed on or Ifixed' to the actuating lever 228, these notches when engagedby the plunger 32G, serving to lock the shaft 221 when set in neutral, direct drive-or over-drive and reverse, respectively, the shaft 221 being show in Fig. 15 as locked in its neutral setting correspendin tothe condition of the transmission when "set as shoWn'in Fig. 1. Thelocking plunger 32B is releasable automatically by the master pedal 3H3 when the latteris depressed, it being connected to this pedal by a .link 32! "which cooperates with a pin 328 fixed to saidpedal. fIn order to enable the master pedal to be operated to an extent suilicien t to over-ride the .master governor and the other-controls"withoutiunlocking the shaft 2235,.or to be=operated.to;.-aifurther extent to shift thecollar I03 sufficien-tlyito'eause control valve it to be fully opened by spring 58, and thereby neutralize thertransrrrission mechanism and to bring. the'zbrake'rings I05 and W5 into engagement, the linl -32l"isprovided with a slot-32% in which thexpin' 328 operates,"the'pin moving idly in this slot while the "master pedal is being depressed to an extent to override the master governor and the other controlsybutpi'ckmg up the end of this slot and' pulling' th'e link 327 and thereby withdrawing the plunger 320 from thenotch .in the segment which it engages,

thereby unlocking the shaft 221 to permit a change in the setting of the transmission, and by depressing the master pedal to its full extent, the friction-ring I on the collar M3 is brought into engagement with the relatively fixed friction ring 06, thereby bringing the rotor to rest or holding it from rotation, and thereby facilitating engagement of the clutch members of the gearing. It is to be noted that while the shiftable clutch member M38 is engaged with the pinion carrier clutch teeth 25 or with the ring gear clutch teeth Hi, the master pedal 3H can be operated to cause the control valve as to be fully opened by spring 58 and thereby neutralize the transmission mechanism and to bring the brake member H35 into contact with brake member to and thereby retard or look the driven or propeller shaft 5 from rotation, thus effectively applying the brake to stop the rear or driving wheels of the motor vehicle.

The operation of the improved transmission is as follows:

Assuming that a sufficient amount of oil or other suitable operating fluid has been placed in the rotor reservoir 22 to bring the oil level therein to near the height of the lower side of the hearing 52, and that the transmission is set in neutral as shown in Fig. 1, starting of the engine will throw all of the oil to the periphery of the rotor reservoir 22, thus forming an annular body of oil which covers the inlets as of the torque pumps carried by the rotor, The rotation of the gear 35 driven from the engine crank shaft 8 causes rotation of the pump drivin gears 34 in the rotor which is then stationary, or substantially so, causing oil to be drawn into the torque pumps through their inlets 3i) and to be exhausted therefrom and returned to the reservoir 22 through the outlet passages 3i into the valve chambers 32. While the transmission is in neutral, the valves 43 and M are held partly closed by the stop spring 64, as shown in Fig. 1'7, thereby causing the rotor to rotate slowly and thereby facilitate meshing of the clutch members of the gearing, but if it is desired to stop rotation of the rotor or relieve any drag on the rotor, the accelerator pedal 26'? is rocked rearwardly thereby causing the collar 38! to engage the upper end of the lever 67 and to rock this lever in a direction to retract the sleeve 53, thus drawin the valves to fully open position, as shown in Fig. 18. Should there be any drag on the rotor after such operation of the accelerator pedal, it may be completely removed by depressing the master pedal 31E], thereby advancing the collar itS sufficiently to engage the friction brake ring i 55 thereon with the stationary brake ring EEG, thereby stopping the rotor and the shaft 1 on which it is mounted.

After rotation of the rotor has been stopped, and while the master pedal (its is held depresse thus holding the plunger 32!] in unlocked relation with the locking sector 326, the transmission may be set in condition for direct or overdrive by rocking the accelerator pedal rearwardly, and by placing the lever ISL! in the notch 933 of the sector I94, and the transmission may then be placed in direct drive by swinging the shift lever 22!! in a direction to cause the shifting arm 23! on the shaft 227 to shift the sleeve HS, and through the spring HQ, the rail 76 from the neutral position shown in Fig. 1 to the direct drive position shown in Fig. 2, the collar I13 fixed to this rail carrying with it the fork I3! and thereby shifting the clutch member I28 from the neutral position shown in Fig. 1 into engagement with the direct drive clutch teeth I21 on the gear lZfi fixed to the driven or propeller shaft 5. By holding the accelerator pedal in its rearwardly rocked position during this setting operation, the collar 30! on the throttle operating rod 27E is pressed against the upper end of the lever 67, thereby withdrawing all of the valves 48 and 4H and holding them in open position as shown in Fig. 18. l'he master pedal Sill may then be released to return to its normal position, thereby re-engaging the plunger 320 with the sector 326 and locking the sleeve I76 from movement.

After setting the transmission as just described, the accelerator pedal may be depressed at its forward or toe end, thereby retracting the collar 30! from the lever 67 and permitting the stop spring 84 to close the valves to a predetermined extent, as for example, to a half-closed position substantially as shown in Fig. 17. Such partial closing of the valves restricts the discharge of fluid through the outlets 3| of the torque pumps, and by gradually increasing the speed of the engine, the output of the pumps is greatly increased and pressure in the fluid is built up in in their outlets, reaction of which resists rotation of the pumps and thereby imparts a torque to the rotor which is commensurate with the output of the torque pumps. Power is thereby transmitted from the driving shaft gear 35 through the pump driving gears E i, and the rotor and the intermediate shaft 7 carrying it, to the main transmission shaft 9, and from the latter to the clutch member l28, clutch teeth l2? and to the driven or propeller shaft 5. While the engine is running, the secondary governor members 16 are thrown outwardly by centrifugal force depending on the position of the accelerator pedal and the extent of the throttle opening, and as the intermediate shaft l begins to rotate, the master governor members 93 are thrown outwardly by centrifugal force, and as the speed of rotation of the intermediate shaft increases, the master governor acts to further close the valves, until the flange 6! comes into contact with the secondary governor members '18 which tend to resist closing of the valves. When the intermediate shaft 7 reaches a speed slightly below the speed of the engine or driving shaft, the master governor members 93 are thrown outwardly with a suiiicient force to overcome the secondary governor members 16 and to complete the closing of the valves, stopping circulation of the torque transmitting fluid and thereby creating a hy-' draulic lock through the torque pumps and transmitting torque from the driving to the driven shaft at equal speed of these shafts. This intercontrol between the master and secondary governors under control of the extent of throttle opening and the position of the accelerator pedal enables the torque transmitted from the driving to the driven shafts to be increased gradually, thereby avoiding abrupt increase of load on the engine or driving member. While the transmision is in operation in direct drive, as described, the governor arms 92 are swung inwardly into the position shown in Fig. 2, thereby locking the sleeve 60 in its closed valve position as shown in this figure due to the overcenter movement of arms 92.

While the transmission is conditioned for direct and overdrive, the brake ring H6 engages the brake teeth H4 on the sleeve H0 on which the reverse gear E20 is fixed, thereby holding this gear from rotation, but allowing the pinions I 2| to rotate idly around this gear. If it is desired to set the transmission in overdrive, this may be accomplished by depressing the accelerator pedal forwardly beyond its fully open throttle position and causing it to depress the plunger 265, which under these conditions will be above the arm 295 of the bell crank lever 286, thereby rocking this bell crank lever and, acting through its linkage therewith, retracting the valve sleeve 55 and thereby pulling the inner valves II into positions to establish communication between the pump discharge ports 3| and 3| a in the rotor hub, and through the ports 42 and 43 in the outer valve 46 which are then held in communication with the ports 3| and 3Ia, and through the port I55 and axial passage I51, as shown in Fig. 20, fluid under pressure from the discharge of the torque pumps being thereby supplied to the cylinder I 55 in the space therein between the piston I63 and the fixed cylinder head I66, the fluid pressure thus introduced into this cylinder actin on the piston to shift the shaft I 45, I 4| to the left in Fig. 2 and correspondingly shifting the clutch member I28 into the position shown in Fig. 3, thereby disengaging it from the direct drive clutch teeth I21 and engaging it with the overdrive clutch teeth I25 on the pinion carrier member Ilsa. Durin this operation, and while the fluid is flowing from the torque pumps into the cylinder I65, pressure of the fiuid in the discharges of the torque pumps drops and thereby momentarily interrupts transmission of torque through the rotor, thus enabling the clutch member I28 to disengage from the direct driving clutch teeth I2! and to engage the overdrive clutch teeth I25. The torque through the rotor is, however, re-established as soon as the cylinder space I65 is filled with oil and the clutch shift has been completed.

During the shift of the clutch member I28 from the direct drive teeth to the overdrive teeth I25, shift of the fork I3I toward the left from the position shown in Fig. 2 to that shown in Fig. 3

causes it to act on the collar I73 fixed on rail Ill) and to compress the spring I19 between it and the shifting sleeve I16, which is loosely mounted on the rail Ill] and is then looked from movement by the plunger 325 which prevents rotation of the shaft 221, the rail I75 being thereby shifted into the position shown in Fig. 3, carrying with it the cam I18 which is pinned thereto, thereby causing the spring-pressed ball 24% to engage in the recess 256 in this cam, the spring 247 which presses the ball 248 into recess 255 of cam I'I8 having sufficient power to move and hold the cam I78 and the rail I to the left as shown in Fig. 3, the spring I19 being thereby loaded to supply power to return the rail I16 to direct drive position, but being restrained by the ball 248 engaging the recess in the cam I18. Shift of the rail I'll) also transfers the plunger 265 from a position above the bell crank 286 as shown in Fig. 2 into a position above the bell crank 265 as shown in Fig. 3, and during such shift of said rail, the separating member 29I prevents dislodgment of the plunger 265 from the bell crank 286 until it has completed its operation, the spring 26I being compressedwhile the plunger 265 is pressed against the side of the member 29I and thereby avoiding obstruction to the shift of the rail I70, and upon return of the forward end of the accelerator pedal to its raised position to permit lifting of the plunger 265', the spring 26I furnishes power to push the lower end of said plunger over the top of the member 29I and into a position at the other side thereof, as shown in Fig. 3. g

If it is desired to shift from overdrive to direct drive, such may be accomplished by merely depressing the accelerator pedal forwardly beyond fully open throttle position, thereby depressing the plunger 265 and causing it to engage and depress the arm 289 of the bell crank lever 285, rocking it in a direction to pull the rod 295 in a direction to shift the collar I53 to the left in Fig. 3, carrying with it the sleeve I00. Such movement of said collar and sleeve causes the cam portion 255 on the hub of the collar to retract and unlock the cam II8 by unloading the spring 221 and loads the spring 254 to store power therein for the return of said collar to the position shown in Fig. 2, and to simultaneously advance the sleeve I06 to retract the master governor members 93 against the action of centrifugal force, causing the arms 92 to be retracted from the flange I6 and thus releasing the sleeve 60 for retraction under the action of the valve opening spring 58 until arrested by the spring 64. The valves 46 and II are thus partially opened, and the depression of the plunger 265, which rocked the bell crank lever 285, also raised the toe 5J6 thereon into engagement with the arm 305 on the lever 67, thereby rocking this lever in a direction and to an extent to retract the sleeve 53, thereby completing the full opening of the valves against the action of the spring 6 1. When the valves are thus fully opened, the torque through the rotor is completely interrupted, after which the spring H9 is free to shift the fork I3I to disengage the clutch member I28, oil or fluid in the cylinder I65 between the piston I63 and cylinder head I66 is exhausted through the axial passage I57, ports I56 and into the valve chambers 32, the ports I56 being then uncovered by the valves 46, as shown in Fig. 18. When the accelerator pedal is permitted to rise or return to throttle controlling position, the plunger 265 is permitted to rise, thus permitting the bell crank lever 285 to return to its normal position and relieving the pull on the rod 295, the latter then releasing the fork I64 and permitting the spring 254 to return the collar I03 to the position shown in Fig. 2 and returning the spring loaded ball 248 to the condition shown in Fig. 2. Return of the collar I03 to the position shown in Fig. 2 also retracts the sleeve I00 from the master governor, thus freeing the latter to function under the action of centrifugal force, and to act on the sleeve 60 to return the valves to closed position, thereby re-establishing transmission of torque through the rotor. Return of the plunger 265 to its raised position also places it above the bell crank lever 286, as shown in Fig. 2, thus setting the transmission in condition for a shift to overdrive.

When it is desired to set the transmission for driving in reverse and direct, the transmission is restored to neutral condition by swinging the shifting lever 225 into neutral position, thus returning the sleeve I76 to its neutral position as shown in Fig. 1, and returning the cam I18 to the position shown in that figure, thus rendering this cam inactive. in the notch I92 in the sector I94, thereby shifting the fork I8! and the rail I'II toward the left ln Fig. l, disengaging the brake teeth II5 on the brake ring IIB from the brake teeth II4 on the sleeve II ll, thus releasing the sun gear I 20, and engaging the brake teeth II! on the brake ring with the brake teeth II8 on the pinion car- The lever I96 is then placed rier member H9, thereby holding the pinioncarrier from rotation and conditioning the transmission for operation in direct and reverse. Such shifting of the rail I H operates the fork I04,

causing it to shift the collar H33 and the sleeve- Ito toward the left in Fig. 1, thereby bringing this sleeve into a position to be engaged by the heels of the master governor members 93, thus permitting the governor to completely close the valves All and il under centrifugal force but not allowing the governor members to assume a looking position such as shown in Fig.- 2. When the master governor is placed in such condition, the above described shift of the rail I'III- to the left also looks the rail I10 and unlocks the rail I12 by shifting the-positions of the plungers 2m and 2H and shifts the interlock lug 286 out of the path of the arm 23I so that it may be shifted from the fork I'Il on the rail I?!) to the fork Hid on the rail H2. The shift lever 220 may then be lifted from its normal lower position, thereby transferring the arm'23I from the former to the latter fork, as described.

With the transmission in the condition just described, if it is desired to set it in reverse,

theshiftv lever 225i is swung in a direction to shift the fork Iilli.v and clutch ring II2 towardthe left in Fig. 1 to cause it to bridge the clutch teethv I I3 on the main transmission shaft 9 and the teeth i If on the sleeve H0, thereby coupling U the sun gear I25] to the main transmission shaft. As the sungear will be thereby rotated in the direction in which the driving shaft and rotor are. rotating, it rotates the pinions I2I meshing therewith in the. opposite or reversedirection, and the engagement of these pinions with the internal gear Itficausesitand the driven orpropeller shaft 5. to be also rotated inthe reverse direction but at a lower speed ratio. The torque may then be transmitted through the rotor; under control of the accelerator pedal, as hereinbefore described.

In order to change the setting-of the transmission from reverse to direct, the shift lever 228is swung in a direction to shift the rail I72 towardptheright from the position. shown in Fig. 9, thereby shifting the transfer memberZfiZ to bring the lug. 2il3;thereon into engagement withthe armitll onthe fork. I3I, and continued movement-of saidrail in said direction carries with it the fork Ill loosely mounted on the rail Iii], thereby, engagingthe clutch member I28 with the direct drive clutch teeth I21 The transmission is then in condition for direct drive, and the torque transmitted is .controlled by the accelerator pedal, as hereinbeforev described. The shift of the rail I72 toward the rightin Fig. 9, as described, carried with it'the arm 255. fixed thereto, thereby bringing it into. contact with the arm 258 which fits loosely over the. rail I10 and is balanced between the springs ZEI and 262. and is connected to the plunger slide 259, thereby shifting the plunger 265zfrom the neutral. position shown in Fig. 1 to the position shown in Fig. 2 above the armlfio .ofthe bell crank 286. Assuming the. automobile or vehicleis being driven in direct. drive, and acceleration thereof beyond the power of the engine obtainable in direct drive is desired, such maybe accomplished by depressing the forward or toe end of the accelerator pedal beyond the fully open throttle position and depressing the plunger 255, thereby engaging it with the bellj crank 288' and rocking this bell crank in. a direction to pullthe rod 298 and with it the lever 20 61, with the result that the sleeve 53 is retracted and with it the valves GI, and through the springs 5'5, the valves 48, against the action of the master governor which is then in non-. locking condition, thereby opening to the desired extent the discharge passages 3I of the torque pumps, similar to that shown in Fig. 1'7. The effect of this is to relieve the pressure of the oil or fluid in the discharge passages of the torque pumps, and to thereby enable the engine to attain a higher speed relatively to that of the rotor. pedal sufficiently to permit the plunger 265. to return to its normal raised position, the valves are permitted to fully close under the influence of the master governor, thereby re-establishing the normal direct drive condition of the transmission.

When it is desired to place the transmission.

mechanism in neutral condition, the setting lever I90 on the segment I94 will be moved beyond the notch I92. This setting of this lever will advance the collar I83, sleeve H30 and extensions Ii'it fixed thereto to the left. The extensions Iii? will pass under the arms 92 of the the governor 533 and immobilize the governor, thus permitting the valve springs 58 to open the valves 40, and by rocking the accelerator pedal 26? in the direction to close the throttle, it will fully open the valves fill as shown in Fig. 18. At the time that the collar I83 was moved to the left, the cam portion 245 of this collar also moved to the left, which allowed the spring plunger 2% to drop and thus relieve the spring tension on spring 24? and ball 248, and thus immobilize the elements which move and hold the cam I18 as previously described. The masterpedal 3 I I] may then be depressed to withdraw the plunger 326 from the segment 326 in Fig. 15. This action permits the shifting lever 220 to move to the neutral position, thereby placing clutch member I28 in a neutral position as shown in Fig. 1 With the clutch member I28 placed in a neutral position, the master pedal 3 I 0 is allowed to return to its normal position, as shown in Fig. 15, and to thus lock the segment 326 and the clutch I28 in said neutral position.

Before the transmission is set in any of the conditions hereinbefore described, the master pedal SIil is first depressed, thereby unlocking the sector 326 fixed on the shifting shaft 221 to permit rotation thereof, and after the selection has been made, the master pedal is permitted to return to its normal position, causing the plunger 328 to lock said shaft.

Although the invention is applicable generally to power transmissions for operating machines or machinery of various kinds, it is particularly advantageous when applied to automotive vehicles employing transmissions of types than the hydraulic type hereinbefore described for controlling the operation thereof. The controlling means' provided by the present invention, when applied to an automobile, enables the transmission thereof to be set selectively for driving in a variable speed range in direct drive, or in reverse, as desirable for driving under. congested traffic conditions as in cities, or to be set selectively for driving in direct or overdrive, as in driving on highways where traffic conditions are less congested and permit of driving at higher speeds. The means for selecting and effecting the different speed changes are intercontrolled, so that the various speed changes may be made with facility and safety,

and in the proper sequence.

By raising the accelerator The novel gearing provided by the present invention, which is applicable to transmissions of types other than the hydraulic type shown, provides a simple and compact structure whereby the driven element of the transmission may be driven selectively in direct or reverse, or direct and overdrive, as desired, by a relatively simple shifting of elements of the gearing.

I claim as my invention:

1. A power transmission mechanism comprising driving and driven elements, meansv including. a torque controlling element interposed between said elements for transmitting torque from the driving to the driven element, a master governor responsive to the speed of the driven element and operative upon said torque controlling element to increase the torque transmitted between said elements, an auxiliary governor responsive to the speed of the driving element and operative upon said torque controlling element to reduce the torque transmitted between said elements in opposition to the influence of the master governor, and means forrestoring the master governor from speed operated condition to inactive condition.

2. A power transmitting mechanism as defined in claim 1, wherein said means for restoring said master governor is controlled manually and locks said master governor in inactive condition.

3. A power'transmission mechanism for an automobile having a fuel control element, comprising driving ancl driven elements, means including a torque controlling element for transmitting torque at variable speed ratios from the driving to the driven element, a master governor responsive to the speed of the driven element and operative upon said controlling element of the torque transmitting means to effect transmission of torque to the driven element at a maxi mum speed ratio, a secondary governor responsive to the speed of the driving element and operative upon said controlling element of the torque transmission to effect transmission of torque to the driven element at a relatively reduced speed ratio, and means operable by the fuel control element of the automobile for restoring the master governor from its fully speed operated position toward inoperative condition and thereby overcoming the influence of the master governor on said controlling element of the torque transmitting means and for setting the latter in condition for transmission of torque at a relatively reduced speed ratio.

4. A power transmission mechanism comprising driving and driven elements, a single hydraulic unit connected to the driving and driven elements for transmitting torque from the driving element to the driven element, including valve means for varying the amount of torque transmitted through said unit and a controlling ele- A ment for said valves, a governor responsive to the speed of the driving element and operative upon said controlling element to place said valve means in a condition to reduce the amount of torque transmitted to the driven element, yieldable means cooperative with said valve means to limit the amount of torque transmitted to the driven element, and a governor responsive to the speed of the driven element and operative upon said valve controlling element with a force superior to the influences thereon of said first-mentioned governor and said torque limiting mean to increase the amount of torque transmitted through said hydraulic unit to the driven element.

5.A power transmission mechanism comprising driving and driven elements, a rotor having means for connecting it to the driven shaft and carrying hydraulic pumps connected to the driving element for circulating a fluid, valves for controlling said circulation of fluid and thereby controlling the transmission of torque through the rotor to the driven element, a governor responsive to the speed of the driving element and operative to open said valves, and a master governor responsive to the speed of the driven element and operative to close said valves in opposition to the first-mentioned governor when the driven element reaches a predetermined speed relatively to that of the driving element.

6. A power transmission mechanism according to claim 5, including a spring acting on said valves with sufiicient force to hold said valves partially open against the action of said firstmentioned governor but with insuflicient force to, resist closing of said valves by said master governor.

7. A power transmission mechanism comprising driving and driven elements, gearing interposed between said elements for connecting them to drive the driven element at lower and higher speed ratios, means for transmitting torque from the driving element to the gearing and having mean for interrupting the transmission of such torque, power operated means for respectively setting the gearing for driving at said speed ratios, and means including a selector having a pair of controlling members for the respective power operated means and for the torque inter= rupting means, and an actuator connected to said setting means for operation in coordination therewith to set the selector for operation of the actuator upon one of said controlling members for interrupting the torque and causing operation of one of said power operated means when the gearing is set for one of said speed ratios, and to set the actuator for operation upon the other of said controlling members to cause operation of the other power operated means to set the gearing for driving at the other of said speed ratios.

8. A power transmission according to claim 7 for an automobile having a fuel control element, wherein said actuator is operative by said fuel control element.

9. A power transmission mechanism comprising driving and driven elements, variable speed gearing interposed between said elements and having a member shiftable to set the gearing i'or relatively higher and lower speeds, means connected to the driving element and the gearing for driving the latter and for interrupting the driving thereof, power means connected to said shiftable member of the gearing for shifting said member to set the gearing for one of said speeds, power means connected to said shiftable member of the gearing for shifting said member to set the gearing for the other speed, and means including a selector having an actuator connected to the shiitable member for setting the selector, by the shifting of said member into a position to set the gearing for the relatively lower speed, for actuation of said interrupting means and for operation of one of said power means to shift said member into a position to set the gearing for the relatively higher speed and for actuation of said interrupting means and for operation of the other of said power means for return of said shifting member to restore the setting of the gearing for the relatively lower speed.

10.. A' 'powerxtransmissioni according. to claim 9 for; an automobile having arraccelerator pedal for controlling .the throttle :of the automobile engine, whereinzsaid actuator is operative .by said accelerator pedal when operated :beyond fully open throttle position.

11.:A power transmission .mechanism :comprising driving and driven elements, direct and overdrive gearing interposed between said elements and having a shiftable member forsetting the gearing for direct or overdrive, power means for shifting: said member to. set the gearing for direct and overdrive respectively, means for driving the gearing from the .driving element and having means for interrupting: such drive, .and a selector comprising. controlling members for controlling said interrupting meansand the respective power means, andan actuating member having means forshifting itwith said .shiitable member of the gearing, when shifted to setthe latter for direct drive, into a position toactuate the controlling member for the powenmeans for shifting saidmember of the gearing to set it for overdrive, and for shifting the actuating member by said shiftable member of the gearing, when shifted to set the latter for overdrive, into a position to actuate the controlling member for the other of said power means for shifting said shiftable member of thegearing to restore the latter for direct drive.

12. A power transmission according to claim 11 for an automobile having a fuelcontrol element, wherein said actuating member is operative by said fuel controlelement.

13. A power transmission according to claim 11 for an automobile having anaccelerator pedal for controlling'the throttle of .the, automobile engine, wherein said actuating member is opera tive by said accelerator pedal when operated beyond fully open throttle position.

14. A power transmission mechanism comprising driving and driven elements, gearing interposed between said elements providing different ratios of speed transmission between said elements, variable torque transmitting means interposed between said e1ements,. agovernor responsive to speed of the driven element for controlling the torque transmitting, means, and means for setting the gearing for difierent speed ratios and coincidently setting the governor in a condition to maintain the torque transmitting means in a predetermined condition when the gearing is set for one speed ratio and for coincidently retracting the governor. in opposition to its response to speed and to set the governor in a condition to permit control of the torque transmitting means when the gearing is set. for another speed ratio.

15. A power transmission .mechanism according to claim 14:, wherein said governor locks said torque transmitting means in said predetermined condition while the governor is in said first-mentioned setting and unlocks said torque transmitting means while the governor is in said secondmentioned setting topermit overriding of the governor and control of the torque transmitting means independently of the overnor.

16. A power transmission mechanism according to claim 14, wherein-said-gearing comprises means which provides a direct drive and an overdrive from said driving to said driven'element, and said first-mentioned setting sets the gearing for overdrive and said second mentioned settingsets the gearing for direct drive.

17. A power transmission mechanism according 24 to claim. 14, including; means controllable: at; the will :of the-operator for'controlling said torque transmitting means-while said governor is set in said .condition to permit controlof said torque transmitting means.

18.. A power transmission mechanism according to claim 14, wherein :said torque transmitting means comprises fluid pressure means, and valves controlling the latter to vary the torque transmitted thereby.

19. A power transmission mechanismaccording to claim 14, wherein .said torque transmitting means comprises hydraulic means for circulating a torque transmitting liquid, and valves controlling such liquid circulation to vary the torque transmitted by said hydraulic means.

20. A power transmission mechanism according to claim 14, wherein said torque transmitting means comprises hydraulic means for circulating a'torque transmitting liquid-and valves controlling such circulation, and including means for holding said valves in closed position by said governor while the latter isset in said predetermined condition and is freed by the governor for opening said valves while said governor is in said second-mentioned setting.

21. A power transmission mechanism for an automobile having throttle controlling means for the engine thereof, comprising a driving element connected to the engine and a driven element, direct and-overdrive gearingbetweensaid elements, a-member for setting the gearing for direct and overdrive for the driven element,

torque transmitting means driven from the driving element-and having-means for varying the amount of torque transmitted'thereby, a governor responsive to the speed of the driven element and cooperative with said torque varying means, means for actuating saidmember in one-direction to set the gearing for overdrive and coincidently setting the governor in a condition to hold said torque varying means in a condition for transmission of -maximumtorque by said torque transmitting means, and means for actuating said member in another direction to set the governor in a condition for operation of saidtorque varying means and to coincidently set the gearing for direct drive, and means controllable by the engine throttle controlling means for operating the torque varying means independently of the governor.

22. A power-transmission mechanism comprising driving and driven-elements, gearing interposed between said elements and having a member for setting the gearing for driving the driven element from the driving element at different speed ratios, torque transmitting means'between said elements having means for varying the amount of torque transmitted by said torque transmitting means and means for interrupting the transmission of torque through said torque transmitting means, a selector comprising a pair of controlling members-for said setting member of the gearing, including means for controlling the torque varying and torque interrupting means respectively, and an actuating member shiftable by said setting member into actuating relation with one or the other'of said controlling members, and means operable by one of the controlling members for actuating the setting member to set the gearing for one speed ratio and coincidently set said actuating member in actuating relation with the other of said controllingmembers, and means operable .by the latter controlling member for actuating the setting member to set the gearing for another speed and coincidently to restore said actuating member to actuating relation with said one of said controlling members.

23. A power transmission mechanism according to claim 22, wherein said gearing embodies means for driving said driven element in direct and overdrive speed ratios relatively tosaid driving element, and said setting member is movable in a direction to set said gearing for direct drive and to coincidently set said actuating member in actuating relation with said controlling member which controls said torque varying means, and said setting member being movable in another direction to set said gearing for overdrive and to coincidently set said actuating member in actuating relation with said controlling member which controls said torque interrupting means.

24. A power transmission mechanism according to claim 22 for an automobile having an accelerator pedal for controlling the throttle thereof, wherein said actuating member is mounted in a position for operation, in each of said settings thereof, by movement of said accelerator pedal beyond the range of its throttle controlling movement.

25. A power transmission mechanism compris ing driving and driven elements, gearing for driving the driven element at different speed ratios, fluid pressure means for changing the setting of the gearing from one speed ratio to another speed ratio, fluid pressure torque transmitting means between said elements, valves op erative to divert fluid pressure from said torque transmitting means to said setting means and for controlling the amount of torque transmitted by said torque transmitting means, controlling members for operating said valves to divert the fluid pressure and to vary the torque respectively, an actuating member for said controlling members, and means for positioning said actuating member in actuating relation with said controlling member for operating the valves to vary the torque ooincidently with the setting of the gearing for one speed ratio and for positioning said actuating member in actuating relation with said controlling member for operating the valves to divert fluid pressure coincidently with the setting of the gear for another speed ratio.

26. A power transmission mechanism comprising driving and driven elements, gearing between said elements for driving the driven element in direct and overdrive speed ratios, a shiftable member for setting the gearing for said speed ratios, hydraulic means for shifting said setting member to set the gearing for said speed ratios,

hydraulic torque transmitting means between said elements, valves operable to divert pressure fluid from said torque transmitting means to said hydraulic means, valves operable to vary the amount of torque transmitted by said torque transmitting means, a pair of controlling members for operating said valves which divert pressure fluid to said'hydraulic means and for operating said valves which vary the tor ue transmitted respectively, and selecting means including an actuating member connected to and shiftable by movement of said setting member in a direction to set the gear ng for direct drive to coincidently position said actuating member in actuating relation with said controlling member for operating the valves which vary the torque transmitted by said torque transmitting means, and shiftable with said setting member by movement of the latter in a direction to set the gear-- ing for overdrive to coincidently position said actuating member in actuating relation with the controlling member for operating the valves which divert pressure fluid to said hydraulic means for shifting the setting member.

27. A power transmission mechanism comprising driving and driven elements, gearing between said elements for connecting them for direct, reverse and overdrive, a pair of reciprocatory rails and cooperating members having means for positioning them to set the gearing in direct and overdrive and in direct and reverse respectively, manually operable means for reciprocating said rails, and a reciprocatory controlling rail operable selectively to control the operative relation of said manually operable means with one or the other of said pair of rails.

28. A power transmission mechanism according to claim 27, wherein said manually operable means for reciprocating said pair of rails comprises an actuating arm shiftable transversely of said rails, and said controlling rail, is provided with means for controlling engagement of said arm with one or the other of said pair of rails, and said actuating arm is rotatable to reciprocate the rail which it engages.

29. A power transmission mechanism comprising driving and driven elements, gearing between said elements for connecting them for a lower or higher forward drive and for reverse drive, means including a pair or" reciprocatory members having means for positioning them to set the gearing for the lower and higher forward drive and for one Of said forward drives and reverse respectively, means selectively engageable with one or the other of said members for actuating it, and a member operable to control the engagement of said actuating means selectively with said pair of members.

30. A power transmission mechanism according to claim 29, including inter-controlling means cooperative with said members and operative by said controlling member to release one of said pair of members for actuation and to prevent actuation of the other of said pair of members.

31. A power transmission mechanism according to claim 29, wherein said pair of members and said controlling member are provided with recesses in their adjacent sides, and including plungers cooperative with the adjacent sides of said members and said recesses therein and controlled by said controlling member to lock one of said pair of members while the other member of said pair is unlocked for actuation.

32. A power transmission mechanism according to claim 29, including means on one member of said pair for setting said gearing for forward and reverse drive, and means operative by reciprocation of said member to set the gearing in neutral when said member is reciprocated to set the gearing for reverse drive.

33. A power transmission mechanism according to claim 29, including means on one member of said pair for setting said gearing for forward and reverse drive, and means operative by reciprocation of said member to neutral position to set the gearing for one Of said forward drives.

34. A power transmission mechanism comprising gearing having elements for setting it for relatively lower and higher forward speeds and for reverse, and a shiftable member for connecting elements of the gearing for said forward speeds, a pair of members for setting elements of the gearing for said lower and higher forward speeds and for one of said forward speeds and 

